EP3124840B1 - Electrically actuated valve - Google Patents

Electrically actuated valve Download PDF

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Publication number
EP3124840B1
EP3124840B1 EP16175891.7A EP16175891A EP3124840B1 EP 3124840 B1 EP3124840 B1 EP 3124840B1 EP 16175891 A EP16175891 A EP 16175891A EP 3124840 B1 EP3124840 B1 EP 3124840B1
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EP
European Patent Office
Prior art keywords
structural element
valve
sealing
damping system
dynamic seal
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EP16175891.7A
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German (de)
French (fr)
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EP3124840A1 (en
Inventor
Herwig Greiner
Werner Schieweck
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Rausch and Pausch GmbH
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Rausch and Pausch GmbH
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Publication of EP3124840A1 publication Critical patent/EP3124840A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F16K31/0658—Armature and valve member being one single element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0693—Pressure equilibration of the armature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/022—Devices for relieving the pressure on the sealing faces for lift valves using balancing surfaces
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1607—Armatures entering the winding

Definitions

  • the present invention relates to an air spring system for a motor vehicle with one or more electrically or electromagnetically actuated valves according to the preamble of claim 1.
  • Valves of the aforementioned type are used in air suspension systems of motor vehicles in various ways and for various functions.
  • valves for filling and emptying the air spring bellows valves for connecting or locking of storage in the system, as well as valves, via which the bellows volume can be connected with additional volume if necessary.
  • valves are actuated electromagnetically, as in the patent DE 10 2011 078 102 A1 described seat valve.
  • Such valves include, inter alia, the three components described in more detail below.
  • a first component which acts as a closure element, can occupy two positions along an axis, wherein in the first position at least one flow is released, which is locked in the second position.
  • a second component surrounds the first, wherein a sealing gap exists between the two components.
  • the third component is a dynamic seal, which is arranged in the sealing gap. It ensures a mutual radial sealing of the first relative to the second component.
  • the patent DE 44 01 215 C1 discloses an angle valve, in particular for vacuum systems, comprising said components and moreover has the described operation.
  • a seal On a first component, which is displaceable along an axis, a seal is fixed.
  • a second component has an inner wall with a conically extending portion and surrounds the first component. If the angle valve is in the open state, then the seal located in the sealing gap is distanced from the conical part of the inner wall of the second component. In the closed state of the valve, the seal is applied to the inner wall of the second component and seals the first and the second component radially against each other.
  • valves are designed as pressure balanced valves. This means that the pressure applied axially on a front side of the closure element is directed to the axially opposite rear side of the closure element.
  • the resulting pressure equalization between the two sides of the closure element on the one hand facilitates the axial displacement of the closure element, and on the other hand it prevents the uncontrolled displacement of the first element, so the closure element, due to different, applied to the opposite sides pressures.
  • the dynamic seal separates in the locked state of the valve on the front and - because of the pressure equalization - in particular also at the back of the closure element pressure from the pressure of that adjacent volume to which the valve blocks the flow.
  • a tandem seal comprises a support body for a radially inner O-ring for sealing inwardly and a radially outer O-ring for sealing to the outside and can be combined with a sliding ring, for example made of PTFE, between an O-ring and the movable component is located.
  • the sliding ring assumes a guiding function for the moving component.
  • an additional guide ring axially adjacent to the seal find application.
  • the patent DE 10 2011 082 007 B3 discloses a special tandem seal comprising a sealing body with two axially spaced, radially outer sealing lips and two axially spaced, radially inner sealing lips, and a support body supporting the sealing body.
  • Object of the present invention is to propose an air spring system for a motor vehicle whose electrically or electromagnetically operated valves require low actuating forces.
  • such a valve has a sealing gap which varies in width depending on the axial position of the closure element. Therefore, one of the two components to which the seal is not fixed, at least one free rotation with a correspondingly reduced or enlarged diameter, wherein the seal in a first axial position of the closure element rests with a sealing lip in the free rotation.
  • the friction of the dynamic seal with the surrounding components depends on the axial position of the displaceable first component. As a result, the required actuating forces also change in proportion to the friction.
  • the sealing lip of the dynamic seal In the second position, ie in the locked state of the valve, the sealing lip of the dynamic seal is outside the free rotation. This guarantees a seal.
  • the sealing effect of the dynamic seal In the first position in which the valve is open, however, the sealing effect of the dynamic seal is not needed; The seal can thus be looser and thus reduced friction sitting in the sealing gap. Optionally, no sealing effect is present in the first position.
  • the sealing gap depending on the axial position of the closure element exactly two different widths, one for each of the two positions.
  • the flow through the valve may include at least one axial flow opening at one end and, for example, at least one radial flow opening at another end, the closure element effecting sealing of the at least one axial flow opening in the second position.
  • the valve is a poppet valve, but the invention is also advantageously applicable to other types of valves, such as spool valves.
  • the dynamic seal is fixed in place in the valve.
  • the component which faces the seal-fixing component has at least one, preferably two, free rotations of reduced or enlarged diameter. Due to the axial fixation of the seal on a component, the sealing gap width can be defined reproducibly in dependence on the axial position of the other component.
  • the dynamic seal has two sealing lips, which sit in the first position in the two free spins and in the second position outside the two free spins.
  • a maximum surface pressure and thus tightness in the second position is guaranteed, while in the first position, the lowest surface pressure and thus the least static friction is present, which (apart from the return spring force) to operate the valve is only overcome.
  • the valve is an electromagnetically actuated valve whose movable armature either forms or is connected to the first displaceable component.
  • the movable magnet armature 7 is part of an iron circle, which also belongs to a stationary pole part 8. Between the armature 7 and the pole piece 8 is a working air gap 9, which allows the magnet armature 7 to move axially in the direction of the pole part 8 when the sealing element 4 in his in Fig. 2 shown closed position is brought. In the locked state, the flow between the radial flow openings 17a, 17b and the axial flow opening 2 is prevented by the sealing element 4 the sealing seat 3 and the dynamic seal 14 closes the flow through the plunger 5 itself.
  • both sealing lips 13a, 13b are located completely outside the free rotations 18a, 18b, as in FIG FIG. 2A shown in greater detail.
  • the dynamic seal 14 thus guarantees a high sealing effect, which is required to block the flow through the pressure balanced hollow plunger 5. Due to the now increased surface pressure of the sealing lips 13a, 13b on the surface of the plunger 5, the friction increases, in particular the static friction. However, no electrical energy is needed to reopen the valve 1, as far as the axial movement of the plunger 5 can be ensured solely by the prestressed spring element 10.

Description

Die vorliegende Erfindung betrifft ein Luftfedersystem für ein Kraftfahrzeug mit einem oder mehreren elektrisch oder elektromagnetisch betätigten Ventilen nach dem Oberbegriff des Anspruchs 1.The present invention relates to an air spring system for a motor vehicle with one or more electrically or electromagnetically actuated valves according to the preamble of claim 1.

Ventile der vorgenannten Art kommen in Luftfedersystemen von Kraftfahrzeugen in verschiedener Weise und für verschiedene Funktionen zum Einsatz. Es existieren beispielsweise Ventile zum Befüllen und Entleeren der Luftfederbälge, Ventile zum Zuschalten oder Sperren von Speichern im System, sowie Ventile, über welche die Balgvolumen mit Zusatzvolumen bei Bedarf verbunden werden können. Bevorzugt werden solche Ventile elektromagnetisch betätigt, so auch das im Patent DE 10 2011 078 102 A1 beschriebene Sitzventil.Valves of the aforementioned type are used in air suspension systems of motor vehicles in various ways and for various functions. There are, for example, valves for filling and emptying the air spring bellows, valves for connecting or locking of storage in the system, as well as valves, via which the bellows volume can be connected with additional volume if necessary. Preferably, such valves are actuated electromagnetically, as in the patent DE 10 2011 078 102 A1 described seat valve.

Derartige Ventile umfassen unter anderem die im weiteren Verlauf genauer beschriebenen drei Bauelemente. Ein erstes Bauelement, das als Verschlusselement fungiert, kann entlang einer Achse zwei Positionen einnehmen, wobei in der ersten Position mindestens ein Durchfluss freigegeben wird, der in der zweiten Position gesperrt ist. Ein zweites Bauelement umgibt das erste, wobei zwischen beiden Bauelementen ein Dichtspalt besteht. Das dritte Bauelement ist eine dynamische Dichtung, die im Dichtspalt angeordnet ist. Sie sorgt für eine gegenseitige radiale Abdichtung des ersten gegenüber dem zweiten Bauelement.Such valves include, inter alia, the three components described in more detail below. A first component, which acts as a closure element, can occupy two positions along an axis, wherein in the first position at least one flow is released, which is locked in the second position. A second component surrounds the first, wherein a sealing gap exists between the two components. The third component is a dynamic seal, which is arranged in the sealing gap. It ensures a mutual radial sealing of the first relative to the second component.

Die Patentschrift DE 44 01 215 C1 offenbart ein Eckventil, insbesondere für Vakuumanlagen, dass die genannten Bauelemente umfasst und darüber hinaus die beschriebene Funktionsweise aufweist. An einem ersten Bauelement, welches entlang einer Achse verschiebbar ist, ist eine Dichtung fixiert. Ein zweites Bauelement weist eine Innenwand mit einem kegelartig verlaufenden Abschnitt auf und umgibt das erste Bauelement. Befindet sich das Eckventil im geöffneten Zustand, so ist die sich im Dichtspalt befindliche Dichtung vom kegelartigen Teil der Innenwand des zweiten Bauelements distanziert. Im geschlossenen Zustand des Ventils liegt die Dichtung an der Innenwand des zweiten Bauelements an und dichtet das erste und das zweite Bauelement radial gegeneinander ab.The patent DE 44 01 215 C1 discloses an angle valve, in particular for vacuum systems, comprising said components and moreover has the described operation. On a first component, which is displaceable along an axis, a seal is fixed. A second component has an inner wall with a conically extending portion and surrounds the first component. If the angle valve is in the open state, then the seal located in the sealing gap is distanced from the conical part of the inner wall of the second component. In the closed state of the valve, the seal is applied to the inner wall of the second component and seals the first and the second component radially against each other.

Meist sind solche Ventile als druckausgeglichene Ventile konstruiert. Das bedeutet, dass der axial auf einer Vorderseite des Verschlusselements anliegende Druck auf die axial gegenüberliegende Rückseite des Verschlusselements geleitet wird. Der dadurch entstehende Druckausgleich zwischen beiden Seiten des Verschlusselements erleichtert einerseits die axiale Verschiebung des Verschlusselements, und andererseits verhindert er die unkontrollierte Verschiebung des ersten Elements, also des Verschlusselements, aufgrund unterschiedlicher, an den gegenüberliegenden Seiten anliegenden Drücken.Most such valves are designed as pressure balanced valves. This means that the pressure applied axially on a front side of the closure element is directed to the axially opposite rear side of the closure element. The resulting pressure equalization between the two sides of the closure element on the one hand facilitates the axial displacement of the closure element, and on the other hand it prevents the uncontrolled displacement of the first element, so the closure element, due to different, applied to the opposite sides pressures.

Die dynamische Dichtung trennt im gesperrten Zustand des Ventils den an der Vorderseite und - wegen des Druckausgleichs - insbesondere auch an der Rückseite des Verschlusselements anliegenden Druck von dem Druck desjenigen angrenzenden Volumens, zu dem das Ventil den Durchfluss sperrt.The dynamic seal separates in the locked state of the valve on the front and - because of the pressure equalization - in particular also at the back of the closure element pressure from the pressure of that adjacent volume to which the valve blocks the flow.

Es kommen dabei unterschiedliche dynamische Dichtungen zum Einsatz. Typische Vertreter dieser Dichtungsart sind Tandemdichtungen, Quadringe oder einfache O-Ringe. Ein Quad-Ring hat anders als ein O-Ring einen in etwa quadratischen oder X-förmigen Querschnitt mit zwei radial außen liegenden und zwei radial innen liegenden, axial zueinander beabstandeten Dichtlippen. Eine Tandemdichtung umfasst dagegen einen Stützkörper für einen radial innen liegenden O-Ring zur Abdichtung nach innen und einen radial außen liegenden O-Ring zur Abdichtung nach außen und kann mit einem Gleitring zum Beispiel aus PTFE kombiniert sein, der zwischen einem O-Ring und dem beweglichen Bauteil liegt. Der Gleitring übernimmt dabei eine Führungsfunktion für das bewegliche Bauteil. Zur Verbesserung der Führungsfunktion kann ein zusätzlicher Führungsring axial benachbart zum Gleitring Anwendung finden. Das Patent DE 10 2011 082 007 B3 offenbart eine spezielle Tandemdichtung, die einen Dichtkörper mit zwei axial beabstandeten, radial außen liegenden Dichtlippen und zwei axial beabstandeten, radial innen liegenden Dichtlippen, sowie einen den Dichtkörper tragenden Stützkörper umfasst.Different dynamic seals are used. Typical representatives of this type of seal are tandem seals, quad rings or simple O-rings. Unlike a O-ring, a quad-ring has an approximately square or X-shaped cross section with two radially outer and two radially inner, axially spaced sealing lips. In contrast, a tandem seal comprises a support body for a radially inner O-ring for sealing inwardly and a radially outer O-ring for sealing to the outside and can be combined with a sliding ring, for example made of PTFE, between an O-ring and the movable component is located. The sliding ring assumes a guiding function for the moving component. To improve the leadership function, an additional guide ring axially adjacent to the seal find application. The patent DE 10 2011 082 007 B3 discloses a special tandem seal comprising a sealing body with two axially spaced, radially outer sealing lips and two axially spaced, radially inner sealing lips, and a support body supporting the sealing body.

Für die dynamische Dichtung in solchen Ventilen ergeben sich verschiedene Anforderungen. Aufgrund der hohen und schwankenden Drücke im Luftfedersystem sind große Anpresskräfte der Dichtung an die sie umgebenden Bauteile erforderlich, um eine ausreichende Dichtigkeit zu gewährleisten. Das führt dazu, dass für die Betätigung der Ventile große Stellkräfte benötigt werden. Der Antrieb eines solchen Ventils muss daher entsprechend viel Energie bereitstellen können, was wiederum zu großen Abmessungen und einem hohen elektrischen Energiebedarf führt. Auch die Montage der Ventile gestaltet sich schwierig, da eine große Kraft bei der Vorspannung der Dichtung erforderlich ist.There are various requirements for the dynamic seal in such valves. Due to the high and fluctuating pressures in the air spring system, large contact pressures of the seal to the surrounding components are required to ensure sufficient tightness. This means that large actuating forces are required for the actuation of the valves. The drive of such a valve must therefore be able to provide correspondingly much energy, which in turn leads to large dimensions and a high electrical energy requirement. Also, the mounting of the valves is difficult, since a large force in the bias of the seal is required.

Aufgabe der vorliegenden Erfindung ist es, ein Luftfedersystem für ein Kraftfahrzeugvorzuschlagen, dessen elektrisch oder elektromagnetisch betätigten Ventile geringe Stellkräfte erfordern.Object of the present invention is to propose an air spring system for a motor vehicle whose electrically or electromagnetically operated valves require low actuating forces.

Diese Aufgabe wird erfindungsgemäß durch ein Luftfedersystem für ein Kraftfahrzeug mit elektrisch oder elektromagnetisch betätigten Ventilen mit den Merkmalen des unabhängigen Anspruchs 1 gelöst. In davon abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung angegeben.This object is achieved by an air spring system for a motor vehicle with electrically or electromagnetically operated Valves with the features of independent claim 1 solved. In dependent claims advantageous embodiments and developments of the invention are given.

Erfindungsgemäß besitzt ein solches Ventil einen in Abhängigkeit zur axialen Lage des Verschlusselements in der Weite variierenden Dichtspalt. Darum weist eines der beiden Bauelemente, an dem die Dichtung nicht fixiert ist, mindestens eine Freidrehung mit dementsprechend verringertem bzw. vergrößertem Durchmesser auf, wobei die Dichtung in einer ersten axialen Position des Verschlusselements mit einer Dichtlippe in der Freidrehung anliegt. Damit hängt die Reibung der dynamischen Dichtung mit den sie umgebenden Bauelementen von der axialen Lage des verschiebbaren ersten Bauelements ab. Das hat zur Folge, dass sich auch die benötigten Stellkräfte proportional zur Reibung ändern.According to the invention, such a valve has a sealing gap which varies in width depending on the axial position of the closure element. Therefore, one of the two components to which the seal is not fixed, at least one free rotation with a correspondingly reduced or enlarged diameter, wherein the seal in a first axial position of the closure element rests with a sealing lip in the free rotation. Thus, the friction of the dynamic seal with the surrounding components depends on the axial position of the displaceable first component. As a result, the required actuating forces also change in proportion to the friction.

In der zweiten Position, also im gesperrten Zustand des Ventils, befindet sich die Dichtlippe der dynamischen Dichtung außerhalb der Freidrehung. Damit ist eine Abdichtung garantiert. In der ersten Position, in der das Ventil geöffnet ist, wird hingegen die Dichtwirkung der dynamischen Dichtung nicht benötigt; die Dichtung kann somit lockerer und damit
reibungsreduziert im Dichtspalt sitzen. Gegebenenfalls ist in der ersten Position keine Dichtwirkung vorhanden.In the second position, ie in the locked state of the valve, the sealing lip of the dynamic seal is outside the free rotation. This guarantees a seal. In the first position in which the valve is open, however, the sealing effect of the dynamic seal is not needed; The seal can thus be looser and thus
reduced friction sitting in the sealing gap. Optionally, no sealing effect is present in the first position.

Die Überwindung der Haftreibung aus einer Ruhelage heraus ist mit erhöhtem Stellenergieaufwand verbunden. In der ersten Position wird diese durch den Sitz der Dichtlippen der dynamischen Dichtung in den entsprechenden Freidrehungen minimiert. Das wiederum hat verschiedene Vorteile. So können die Abmessungen und die Leistung der Antriebseinheit verringert werden, bei zugleich schnellerer Ventilschaltzeit. Der elektrische Energiebedarf wird gesenkt. Auch die Montage des Ventils wird vereinfacht, da die Vorspannkräfte der Dichtung in bestimmten Bereichen des Ventils verringert sind.Overcoming the static friction from a rest position is associated with increased expenditure of energy. In the first position, this is minimized by the seating of the sealing lips of the dynamic seal in the respective free spins. That in turn has several advantages. Thus, the dimensions and performance of the drive unit can be reduced, while at the same time faster valve switching time. The electrical energy requirement is lowered. Also, the assembly of the valve is simplified because the biasing forces of the seal are reduced in certain areas of the valve.

Vorzugsweise weist der Dichtspalt in Abhängigkeit zur axialen Lage des Verschlusselements genau zwei unterschiedliche Weiten auf, eine für jede der beiden Positionen.Preferably, the sealing gap depending on the axial position of the closure element exactly two different widths, one for each of the two positions.

Der Durchfluss durch das Ventil kann an einem Ende mindestens eine axiale Durchflussöffnung und an einem anderen Ende zum Beispiel mindestens eine radiale Durchflussöffnung aufweisen, wobei das Verschlusselement in der zweiten Position eine Abdichtung der mindestens einen axialen Durchflussöffnung bewirkt. Vorzugsweise handelt es sich bei dem Ventil um ein Sitzventil, aber die Erfindung lässt sich vorteilhaft auch auf andersartige Ventile anwenden, zum Beispiel Schieberventile.The flow through the valve may include at least one axial flow opening at one end and, for example, at least one radial flow opening at another end, the closure element effecting sealing of the at least one axial flow opening in the second position. Preferably, the valve is a poppet valve, but the invention is also advantageously applicable to other types of valves, such as spool valves.

Üblicherweise ist die dynamische Dichtung ortsfest in dem Ventil fixiert. Dementsprechend weist das dem die Dichtung fixierenden Bauelement gegenüberliegende Bauelement mindestens eine, vorzugsweise zwei, Freidrehungen mit verringertem bzw. vergrößertem Durchmesser auf. Durch die axiale Fixierung der Dichtung an einem Bauelement kann die Dichtspaltweite in Abhängigkeit zur axialen Lage des anderen Bauelements reproduzierbar festgelegt werden.Usually, the dynamic seal is fixed in place in the valve. Accordingly, the component which faces the seal-fixing component has at least one, preferably two, free rotations of reduced or enlarged diameter. Due to the axial fixation of the seal on a component, the sealing gap width can be defined reproducibly in dependence on the axial position of the other component.

Vorzugsweise verfügt die dynamische Dichtung über zwei Dichtlippen, die in der ersten Position in den zwei Freidrehungen und in der zweiten Position außerhalb der beiden Freidrehungen sitzen. Damit ist eine maximale Flächenpressung und somit Dichtheit in der zweiten Position garantiert, während in der ersten Position die geringste Flächenpressung und damit auch die geringste Haftreibung vorliegt, die (abgesehen von der Rückstellfederkraft) zur Betätigung des Ventils nur noch zu überwinden ist.Preferably, the dynamic seal has two sealing lips, which sit in the first position in the two free spins and in the second position outside the two free spins. Thus, a maximum surface pressure and thus tightness in the second position is guaranteed, while in the first position, the lowest surface pressure and thus the least static friction is present, which (apart from the return spring force) to operate the valve is only overcome.

Vorzugsweise handelt es sich bei dem Ventil um ein elektromagnetisch betätigtes Ventil, dessen beweglicher Anker entweder das erste verschiebbare Bauelement bildet oder mit diesem verbunden ist.Preferably, the valve is an electromagnetically actuated valve whose movable armature either forms or is connected to the first displaceable component.

Nachfolgend wird die Erfindung beispielhaft anhand der anhängenden Figuren dargestellt. Darin zeigen:

  • Fig. 1 ein elektromagnetisches Sitzventil für ein Luftfedersystem eines Kraftfahrzeugs gemäß einem bevorzugten Ausführungsbeispiel im geöffneten Zustand,
  • Fig. 1A einen vergrößerten Ausschnitt des Ventils aus Fig. 1,
  • Fig. 2 das Ventil aus Fig. 1 im gesperrten Zustand,
  • Fig. 2A wiederum einen vergrößerten Ausschnitt des Ventils aus Fig. 2, und
  • Fig. 2B eine vergrößerte Darstellung einer Freidrehung am Stößel.
Das in Fig. 1 im geöffneten Zustand und in Fig. 2 im gesperrten Zustand dargestellte Sitzventil 1 besitzt eine Ventilöffnung 2 mit einem Dichtsitz 3, welches durch ein Dichtelement 4 verschließbar ist. Die Dichtfläche des Dichtelements 4 ist elastisch verformbar, um eine zuverlässige Abdichtung der axialen Durchflussöffnung 2 zu gewährleisten. Das Dichtelement 4 sitzt am vorderen axialen Ende eines Stößels 5, der über eine Verbindungsstange 6 mit einem beweglichen Magnetanker 7 gekoppelt ist. Es ist prinzipiell denkbar, das Dichtelement 4 unmittelbar am Magnetanker 7 zu befestigen. Im dargestellten Ausführungsbeispiel sitzt der Stößel 5 jedoch fest auf der Verbindungsstange 6, welche wiederum fest im Magnetanker 7 sitzt. Dadurch ergibt sich eine bewegliche Baugruppe bestehend aus Dichtelement 4, Stößel 5, Verbindungsstange 6 und Magnetanker 7. Der Stößel 5 selbst ist hohl. Durch ihn wird der an der Vorderseite des Dichtelements 4 anliegende Druck auf die Rückseite des Stößels 5 geleitet, sodass oberhalb einer dynamischen Dichtung 14 und unterhalb des Dichtelements 4 derselbe Druck anliegt. Der Stößel 5 ist von einem zweiten Bauelement 15 umgeben. Zusammen spannen sie einen Umfangsdichtspalt 16 auf, in dem die dynamische Dichtung 14 sitzt und in radiale Richtung abdichtet.The invention will now be described by way of example with reference to the attached figures. Show:
  • Fig. 1 an electromagnetic seat valve for an air spring system of a motor vehicle according to a preferred embodiment in the open state,
  • Fig. 1A an enlarged section of the valve Fig. 1 .
  • Fig. 2 the valve off Fig. 1 in the locked state,
  • Fig. 2A again an enlarged section of the valve Fig. 2 , and
  • Fig. 2B an enlarged view of a free rotation on the plunger.
This in Fig. 1 in the open state and in Fig. 2 Poppet valve 1 shown in the locked state has a valve opening 2 with a sealing seat 3, which is closable by a sealing element 4. The sealing surface of the sealing element 4 is elastically deformable in order to ensure a reliable sealing of the axial flow opening 2. The sealing element 4 is seated at the front axial end of a plunger 5, which is coupled via a connecting rod 6 with a movable armature 7. It is in principle conceivable to fasten the sealing element 4 directly on the magnet armature 7. In the illustrated embodiment, however, the plunger 5 sits firmly on the connecting rod 6, which in turn sits firmly in the armature 7. This results in a movable assembly consisting of sealing element 4, plunger 5, connecting rod 6 and armature 7. The plunger 5 itself is hollow. Through it, the voltage applied to the front side of the sealing element 4 pressure is passed to the back of the plunger 5, so above a dynamic seal 14 and below the sealing element 4 bears the same pressure. The plunger 5 is from a surrounded second component 15. Together, they clamp a circumferential sealing gap 16, in which the dynamic seal 14 is seated and seals in the radial direction.

Der bewegliche Magnetanker 7 ist Teil eines Eisenkreises, dem auch ein ortsfestes Polteil 8 zugehört. Zwischen dem Magnetanker 7 und dem Polteil 8 liegt ein Arbeitsluftspalt 9, der es dem Magnetanker 7 ermöglicht, sich axial in Richtung auf das Polteil 8 zuzubewegen, wenn das Dichtelement 4 in seine in Fig. 2 dargestellte Schließposition gebracht wird. Im gesperrten Zustand wird der Durchfluss zwischen den radialen Durchflussöffnungen 17a, 17b und der axialen Durchflussöffnung 2 unterbunden, indem das Dichtelement 4 den Dichtsitz 3 und die dynamische Dichtung 14 den Durchfluss durch den Stößel 5 selbst verschließt.The movable magnet armature 7 is part of an iron circle, which also belongs to a stationary pole part 8. Between the armature 7 and the pole piece 8 is a working air gap 9, which allows the magnet armature 7 to move axially in the direction of the pole part 8 when the sealing element 4 in his in Fig. 2 shown closed position is brought. In the locked state, the flow between the radial flow openings 17a, 17b and the axial flow opening 2 is prevented by the sealing element 4 the sealing seat 3 and the dynamic seal 14 closes the flow through the plunger 5 itself.

In der in Fig. 1 dargestellten geöffneten Schaltstellung des Ventils wird der Magnetanker 7 durch mechanische Belastung mittels eines Federelements 10 beabstandet zum Polteil 8 gehalten. Wie die vergrößerte Darstellung gemäß Figur 1A zeigt, liegen dabei die beiden Dichtlippen 13a, 13b der dynamischen Dichtung 14 an Freidrehungen 18a, 18b des Stößels 5 an. Das hat zur Folge, dass sowohl die Dichtwirkung als auch die Reibung gering sind.In the in Fig. 1 shown open switching position of the valve, the armature 7 is held by mechanical load by means of a spring member 10 spaced from the pole piece 8. As the enlarged view according to Figure 1A shows, while the two sealing lips 13a, 13b of the dynamic seal 14 at free rotations 18a, 18b of the plunger 5 at. This has the consequence that both the sealing effect and the friction are low.

Durch elektrische Bestromung einer den Magnetanker 7 und das Polteil 8 umgebenden Spule 11 wird ein den Magnetanker 7 und das Polteil 8 durchsetzender Magnetkreis in der Weise erzeugt, dass zwischen dem Polteil 8 und dem Magnetanker 7 eine magnetische Anziehungskraft wirkt, die der mechanischen Belastung des Federelements 10 entgegenwirkt und diese überwindet. Der Magnetanker 7 bewegt sich dann über den Arbeitsluftspalt 9 auf das Polteil 8 zu, so dass der Stößel axial verschoben wird und das Dichtelement 4 den Dichtsitz 3 verschließt. Dabei reduziert der lockere Sitz der dynamischen Dichtung 14 die zu überwindende Haftreibung erheblich. Zur axialen Verschiebung des Stößels 5 aus seiner Ruhelage heraus wird somit vergleichsweise wenig elektrische Energie benötigt. Während des Schließvorgangs werden die Dichtlippen 13a, 13b der dynamischen Dichtung 14 aus den Freidrehungen 18a, 18b des Stößels 5 auf einen größeren Durchmesser geschoben, sodass die Dichtwirkung der dynamischen Dichtung 14 zunimmt.By electrical energization of a magnet armature 7 and the pole part 8 surrounding coil 11, a magnet armature 7 and the pole part 8 enforcing magnetic circuit is generated in such a way that between the Pole 8 and the armature 7, a magnetic attraction acts, which counteracts and overcomes the mechanical stress of the spring element 10. The magnet armature 7 then moves over the working air gap 9 toward the pole part 8, so that the tappet is displaced axially and the sealing element 4 closes the sealing seat 3. The loose fit of the dynamic seal 14 significantly reduces the static friction to be overcome. For the axial displacement of the plunger 5 from its rest position thus comparatively little electrical energy is needed. During the closing operation, the sealing lips 13a, 13b of the dynamic seal 14 are pushed from the free rotations 18a, 18b of the plunger 5 to a larger diameter, so that the sealing effect of the dynamic seal 14 increases.

Im geschlossenen Zustand des Ventils 1 sitzen beide Dichtlippen 13a, 13b vollständig außerhalb der Freidrehungen 18a, 18b, wie in Figur 2A in größerem Detail gezeigt. Die dynamische Dichtung 14 garantiert so eine hohe Dichtwirkung, die benötigt wird, um auch den Durchfluss durch den druckausgeglichenen hohlen Stößel 5 zu sperren. Aufgrund der nun erhöhten Flächenpressung der Dichtlippen 13a, 13b an der Oberfläche des Stößels 5, erhöht sich die Reibung, insbesondere die Haftreibung. Jedoch wird zur erneuten Öffnung des Ventils 1 keine elektrische Energie benötigt, da insoweit die axiale Bewegung des Stößels 5 alleine durch das vorgespannte Federelement 10 gewährleistet werden kann.In the closed state of the valve 1, both sealing lips 13a, 13b are located completely outside the free rotations 18a, 18b, as in FIG FIG. 2A shown in greater detail. The dynamic seal 14 thus guarantees a high sealing effect, which is required to block the flow through the pressure balanced hollow plunger 5. Due to the now increased surface pressure of the sealing lips 13a, 13b on the surface of the plunger 5, the friction increases, in particular the static friction. However, no electrical energy is needed to reopen the valve 1, as far as the axial movement of the plunger 5 can be ensured solely by the prestressed spring element 10.

Claims (8)

  1. An air damping system for a motor vehicle, comprising at least one electrically or electromagnetically actuated valve (1), having:
    - a first structural element (5) which can assume two positions by displacement along an axis, wherein in the first position at least one flow is released, which is blocked in the second position,
    - a second structural element (15) surrounding the first structural element (5), wherein a circumferential sealing gap (16) exists between the two structural elements (5, 15),
    - a dynamic seal (14), comprising a sealing lip (13), wherein the dynamic seal (14) is arranged in the circumferential sealing gap (16) and axially fixed on one of the two structural elements (5, 15), in at least one axial position of the first structural element (5) mutually seals the two structural elements (5, 15) radially, and slides over a surface of one of the two structural elements (5, 15) upon the axial displacement of the first structural element (5),
    characterized in that that one of the two structural elements (5, 15) to which the dynamic seal (14) is not fixed has at least one recess (18) with correspondingly reduced or increased diameter, in which the sealing lip (13) of the dynamic seal (14) is disposed in the first position of the first structural element (5), wherein the sealing lip (13) in the second position of the first structural element (5) is disposed outside said at least one recess (18) and mutually seals the two structural elements (5, 15) radially.
  2. The air damping system according to claim 1, characterized in that the valve (1) is a pressure-compensated valve (1), wherein a pressure present axially on a front side of the first structural element (5) is passed to the axially opposing back side of the first structural element (5), so that a pressure compensation occurs between the front and back sides of the first structural element (5).
  3. The air damping system according claim 1 or 2, characterized in that the sealing gap (16) has exactly two different widths.
  4. The air damping system according to any of claims 1 to 3, characterized in that the at least one flow comprises at one end at least one axial flow opening (2), and that the first structural element (5) effectuates a sealing of the at least one axial flow opening (2) in the second position.
  5. The air damping system according to claim 4, characterized in that the valve (1) is a seat valve.
  6. The air damping system according to any of claims 1 to 5, characterized in that that one of the two structural elements (5, 15) on which the dynamic seal (14) is not fixed has two recesses (18a, 18b) with correspondingly reduced or increased diameter.
  7. The air damping system according to any of claims 1 to 6, characterized in that the dynamic seal (14) has two sealing lips (13a, 13b).
  8. The air damping system according to any of claims 1 to 6, characterized in that the valve (1) is an electromagnetically actuated valve (1) whose movable armature (7) either forms the first structural element (5) or is connected to the first structural element (5).
EP16175891.7A 2015-07-28 2016-06-23 Electrically actuated valve Active EP3124840B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015112328.2A DE102015112328A1 (en) 2015-07-28 2015-07-28 Electrically actuated valve

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EP3124840A1 EP3124840A1 (en) 2017-02-01
EP3124840B1 true EP3124840B1 (en) 2019-05-08

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EP16175891.7A Active EP3124840B1 (en) 2015-07-28 2016-06-23 Electrically actuated valve

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US (1) US10119626B2 (en)
EP (1) EP3124840B1 (en)
DE (1) DE102015112328A1 (en)

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KR102371012B1 (en) * 2017-09-08 2022-03-04 현대자동차주식회사 Fuel supplying valve for fuel cell system
JP7360723B2 (en) 2021-02-04 2023-10-13 株式会社不二工機 electrically driven valve
US11719349B2 (en) 2021-11-16 2023-08-08 Mueller Refrigeration, LLC Axial three-way modulating valve

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DE4401215C1 (en) * 1994-01-18 1995-03-23 Vat Holding Ag Angle valve
DE19652410C2 (en) * 1996-12-06 1999-12-09 Mannesmann Ag Electropneumatic valve
US5897119A (en) * 1997-04-18 1999-04-27 Garlock, Inc. Floating wiper seal assembly
DE19955886A1 (en) * 1999-11-20 2001-05-23 Bosch Gmbh Robert Solenoid valve with a check valve
US7857282B2 (en) * 2003-02-05 2010-12-28 Continental Teves Ag & Co., Ohg Solenoid valve
US20040195778A1 (en) * 2003-04-04 2004-10-07 Smith Oscar M. Resilient mount and shaft seal for motor
DE102005061509B4 (en) * 2005-05-06 2014-08-07 Continental Teves Ag & Co. Ohg Solenoid valve
JP2009525424A (en) * 2006-02-02 2009-07-09 ボーグワーナー・インコーポレーテッド Turbocharger
DE602007002404D1 (en) * 2007-07-20 2009-10-22 Fiat Ricerche System and method for controlling a solenoid valve, in particular for a system for variable actuation of the valves of an internal combustion engine according to Mehrfachhubmodus
DE102010021395B4 (en) * 2010-05-25 2022-05-19 Schaeffler Technologies AG & Co. KG solenoid valve
DE102011078102C5 (en) 2011-06-27 2019-03-28 Rausch & Pausch Gmbh Electromagnetically actuated seat valve
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Also Published As

Publication number Publication date
US20170030475A1 (en) 2017-02-02
US10119626B2 (en) 2018-11-06
DE102015112328A1 (en) 2017-02-02
EP3124840A1 (en) 2017-02-01

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